Variable-speed transmission



Nov. 25, 1947. R. D. MORSE 3 4 VARIABLE SPEED TRANSMISSION Filed June 19, 1945 4 Sheets-Sheet 1 ATTORNEYS NOV. 25, 1947. R. D. MORSE 2,431,494

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INVEN TOR.

w. m M Q 7 W P Mfla ATTORNEYS 15 F g k Patented Nov. 25, 1947 UNETED STATES PATENT OFFICE- VARIABLE-SPEED TRANSMISSION Robert D. Morse, Monroe, Mich. Application June 19, 1945, Serial No. 600,391

4 Claims. (Cl. 74-23017) This invention relates tovariable ratio v belt power transmitting equipment and in particular to means for positively varying the pitch diameter of cooperating V-belt pulleys.

Variable ratio V-belt drives are in use where moderate changes in speed ratios are required and the speed ratio does not have to be precisely maintained. The ordinary method of varying the pitch diameter of a V-belt pulley is to slidably mount half of the pulley on the shaft and to hold it in position against the wedging action of a V-belt by means of a thrust bearing. This type of construction results in an end thrust being transmitted to the shaft carrying the other half of the pulley and suitable thrust'bearings must be provided to carry this thrust. The use of thrust bearings suffers a disadvantage that it is difficult to precisely position the halves of a pulley with respect to each other and to maintain that spacing under wide variations in load.

The object of this invention'is to provide positive means for positioning the halves of a variable ratio V-belt pulley with respect to each other.

Another object is to provide a variable ratio I V-belt pulley assembly in which no axial thrust is transmitted to the bearings journaling the shafts. A

Another object of the invention is to provide gearing connecting the pitch diameter adjusting means on each of two shafts such that the pulley halves on the two shafts will be moved precisely equal and opposite distances when a change in ratio is effected.

These. and other objects and advantages are apparent from the following description and drawings showing specific embodiments of the invention.

According to the invention the axial spacing between the halves of a variable ratio ,V-belt transmission pulley is controlled and adjusted by means of threaded members acting between the pulley halves and the shaft. The threaded members and the shaft are connected through a differential gear train which permits the threaded means and the shaft to rotate synchronously as long as the adjusting gear is stationary but which produce relative rotation between the threaded means and the shaft when the adjusting gear is moved.

The invention further contemplates suitably shaping the faces of the pulley halves so that 2 embodying the invention are shown in the accompanying drawings.

In the drawings:

Figure I is a plan view partly in section and with parts broken away, of a variable ratio V-belt transmission embodying the improved ratio adjusting means.

Figure 11 is a vertical section of a V-belt transmission taken substantially along the line IIII of Figure I.

. Figure III is a vertical section taken substantially along the line III-III of Figure I.

Figure IV is a fragmentary plan view showing another method of positioning the pulley halves of a V-belt transmission.

Figure V is'a fragmentary plan view partly in section showing another gear train suitable for use in adjusting the pitch diameter of the pulleys of a V-belt transmission,

Figure V1 is a fragmentary plan view of still another form of gear practicing the invention.

uniform belt tension is maintained as the speed ratio is varied from maximum to minimum.

Examples of variable ratio I-belt transmissions Figure VII is a diagram illustrating the computation of the length of belt required.

Figure VIII is a diagram illustrating the computation of one shape .of pulley for maintaining constant belt tension.

These specific figures and the accompanying description are intended merely to disclose and illustrate the invention and not to impose limitations upon the claims.

In the first example of a variable ratio V-belt transmission embodying the invention an input shaft l and an output shaft 2 are journaled in bearings located in the walls of a housing 3. The housing 3 is divided into two compartments 4 and 5 by a transverse wall 6 extending perpendicularly to the parallel input and output shafts l and 2. A series of threaded sleeves l are keyed to that portion of the input shaft l which extends across the chamber 4. The sleeves I having alternately right and left hand threads carry a plurality of pulley halves 8 and 9, the halves 8 being threaded on the right hand sleeves and the halves 9 bein threaded on the left hand sleeves. The halves 8 and 9 are maintained in rotational alignment by a series of rods Ill which extend axially through holes drilled in the pulley halves 8 and 9 and which are secured in an adjusting member ll journaled on the shaft I in the plane of the dividing wall 6. Oil seals l2 bearing on the periphery of the adjusting member ll prevent any flow or leakage of lubricating oil from the chamber 5 into the chamber 4.

train suitable for usein 3 The output shaft 2 in a space within the chamber 4 has a series of'threaded sleeves I3 keyed thereto. The sleeves I3, similar to the sleeves 1, have alternately right and left hand threads which mesh with corresponding threads in the hubs of pulley halves I4 and I5. The pulley halves l4 are threaded on the left hand sleeves I3 while the pulley halves I5 are threaded on right hand sleeves. Another series of rods I8 similar to the rods III are fitted through the pulley halves I4 and I5 and secured in an adjusting member I1 journaled on the output shaft 2. I V-belts I8 trained over the pulleys formed of the pulley halves 8 and 9 and those formed by the pulley halves I4 and I5 transmit power from the input shaft I to the output shaft 2. v

When either of the adjusting members H or I1 is rotated with respect to the shaft on which it is journaled the pulley halves are rotated with For example,

respect to the threaded sleeves. rotation of the input shaft I clockwise as viewed from the right end of the shaft as seen in Figure I, While holding the adjusting member II stationary, causes the pulley halves 8 and to approach each other thereby increasing the pitch diameter of the V-pulleys formed thereby. Sim-.

ilarly, clockwise rotation of the output shaft 2 with respect to its adjusting member I1 separates the pulley halves I4 and I5 thereby decreasing their effective pitch diameters.

When the speed ratio is not being changed the adjusting members and the shafts must rotate at exactly the same'veloeity. According to the invention this synchronous rotation of the drive shaft l and the adjusting member II is secured by a differential gear train.

The gear train comprises a beveled gear I9 keyed to the shaft I and meshing with a pair of idler pinions 20 journaled on studs 2I projecting laterally from a sleeve 22. The sleeve 22 is loosely journaled on the shaft I and carries a spur gear 23. The spur gear 23 in turn meshes with a pinion 24 keyed to a short shaft 25 which is journaled in a pair of pedestals 26. The other end of the short shaft 25 carries another spur gear 21 meshing with a gear 28 keyed to the adjusting member I I.

The idlers 20 which mesh with the bevel gear I9 keyed to the shaft I also mesh with a bevel gear 29 the same as the bevel gear'I9 except that it is formed on the side of a worm wheel 30 which is journaled on the sleeve 22. The worm wheel 30 meshes with a worm 3| (Figure 111) which is carried on a shaft 32 extending through the chamber 5 transversely to the input and output shafts I and 2. As long as the worm wheel 30 is held stationary, i. e., no change in pitch diameter of the pulleys is being made, rotation of the shaft I driving through the bevel gear I9 and the idlers 20 rotates the sleeve 22 at half the speed of the input shaft I. The rotation of the sleeve 22 is transmitted through the gear train comprising the pairs of gears 23, 24 and 21, 28 to drive the adjusting member II. The gears 23, 24, 21 and 28 are designed to provide a two-to-one increase in speed so that the half speed rotation of the sleeve 22 appears as full speed rotation of the gear 28 and adjusting member ll. Therefore, as long as the worm wheel 30 is held stationary no relative rotation takes place between the input shaft I and the adjusting member II and'consequently there is no change in pitch diameter of the pulleys formed by the pulley halves 8 and 9.

If the input shaft I is held stationary and the I half speed rotation is transmitted through the A series of gears 23, 24, 21 and 28 to provide rotation of the gear'28 and the adjusting member II attached thereto in'the same direction and at the same speed as the worm'wheel 30. Thus, when the shaft I is stationary and the worm wheel 30 is rotated relative rotation occurs between the adjusting member I I and the sleeves 1 keyed to the shaft I so that the pitch diameter of the pulleys is changed accordingly.

It is not necessary that the shaft I be held stationary while the worm wheel 30 is rotated because the effect of each motion on the rotation of the adjusting member II is'independent of the other. a

The output shaft 2 is supplied with a similar gear train for rotating its adjusting member 41 with respect to theshaft 2. A worm wheel 33 of this gear train-the counterpart of the worm wheel 3Il-meshes with a worm 34 on the worm shaft 32 (Figure .111). Rotation of the worm shaft 32 rotates the worm wheels 30 and 33 equal amounts thus producing equal relative rotations between the adjusting members II and I1 and the shafts I and 2. The pitch of the threads on the sleeves 1 and I3 arethe same, therefore the axial shift of the pulley halves 8 and 9 is exactly equal and opposite to the axial shift of the pulley halves l4 and I5 so that precise adjustment of the pitch diameter may be readily controlled.

Changes in pitch may be accomplished by manually rotating the worm shaft 32 or by driving r it with a pitch changing motor 35 as indicated in thrust exerted by the wedging action of 'the V- belts is absorbed within the shaft itself and does not exert any thruston the bearings journaling the shaft. Therefore there are no thrust bearings to wear or to get out of order. The wedging action of the V- belts also introduces friction between the pulley halves and the threaded sleeves so that'the greater part of the torque being transmitted by the belt; to either of the shafts is carried through the friction of the pulley halves on the threads rather than through the aligning rods I 0 and the gear train. The gear train thus runs with little or no load except when changesin pitch diameter are being made.

In the next example of the invention pulley halves 36 and 31 are mounted directly on an input shaft 38 which is journaled in a housing 39. The housing 39 is divided into a belt chamber" and gear chamber 4| by a transverse partition 42. The pulley halves 31 are spaced along and rigidly fastened to the input shaft 38 while the pulley halves 36 are slidable along a spline in the shaft 38. The several halves 36 are attached together by a series of rods 43 which pass through holes 44 .in the rigidly mounted halves 31. The rods 43 after passing through a sealing ring 45 are secured in a nut 46 which is screwed onto the threaded hub 41 of a bevel gear 48. As in the previous example a gear train is provided for adjusting and maintaining the relative rotary positions of the shaft 38 and the threaded hub 41.

In this example a bevel gear 43 keyed to the shaft 38 meshes with bevel idler gears 50 Jourdriving an idler 51 prises a bevel pinions journaled on naled on studs 5| extending laterally from a sleeve 52 Journaled on the shaft 30. The sleeve with an inner row of teeth 54 of'a bevel gear 55 which is journaled on the sleeve 52. The inner row of teeth 54 corresponds in number to the teeth of the bevel gear 49 while an 'outer row of teeth 55 of the bevel gear 55-meshing with and mounted on a stationary stud shaft 58 corresponds in number to the teeth of the gear 48. The idler 51 engages the bevel gear 48 whose threaded hub axially positions the nut 46 attached to the V-pulleys.

In this train of gears when the worm wheel 53 is held stationary and the input shaft 38 is rotated the first bevel gear 49 rotates with the shaft thereby driving the idlers 50. The idlers 50, whose axes are held stationary by the worm wheel 53, drives the bevel gear 55 in the opposite direction at the same speed as the input shaft 38. The outer row of teeth of the bevel gear 55, driving through the idler 51 whose axis is fixed, drives the bevel gear 48 in the opD$ite direction to the bevel gear 55 and consequently in the same direction as and at the same speed as the bevel gear 49 which is keyed to the shaft 38. If the input shaft 38 is held stationary and the worm wheel 53 is rotated, thereby rotating the axes of the idlers 50, the bevel gear 55 is turned in the same direction and twice as fast as the worm wheel. The rotation of the bevel gear 55 transmitted through the idler 51 rotates the bevel gear 48 in the opposite direction to and at the same speed as the bevel gear 55 thereby producing two revolutions of the bevel gear 48 with respect to the shaft 38 for each revolution of the worm wheel 53. The relative rotation between the threaded hub of the bevel gear 48 and the nut 46 which is held fixed by the rods 43 produces axial motion of the nut 45 and the movable halves 35 of the V-pulleys.

This pitch changing assembly is duplicated on the output shaft except that the left hand half of each pulley is fixed to the shaft and the right hand half is moved by its adjusting nut operating through connecting rods similar to the rods 43. By moving one half of each of the opposite cooperating pulleys equal amounts and in the same direction pitch changes of the pulleys are effected 'without disturbing the belt alignment because the belt in assuming its new position moves half as far as the pulley halves. This assembly has the same desirable characteristic in that no thrust produced by the wedging action of the V-belts is transmitted to the bearings journaling either the input or the output shaft. Furthermore, in this example the pulley halves are all keyed to the shaft so that there is no possibility of any of the transmitted power being transmitted through the gear train.

The gears in the gear train may be rearranged to provide a somewhat more compact structure as is shown in Figure V. In this example, illustrated with the same type of pulley holding elements as the first example, the geartrain comgear 59 keyed to an input shaft meshes with bevel idler studs extending inwardly from arms 52 of a worm wheel 63 which is loosely journaled on the shaft 60. When the worm wheel 53 is held stationary and the input shaft 50 is 50. The bevel gear 59 .faced bevel gear 84 which is also journaled on the shaft 60. The second face of the bevel gear 54 driving through an idler pinion 55 journaled on a stationary stud 55 rotates a bevel pinion 61 which is keyed to a. pulley adjusting member 68. The pulley adjusting member 68 carries a series of rods 65 by which it may rotate the, pulley halves forming the V- pulleys on threaded sleeves so as to change-their axial spacing. In this ex ample the bevel gears 59, 54 and 51 have each the same number of teeth and since there are two reversals of direction through the idler pinions BI and 85 it is apparent that the bevel gear 61 and the adjusting member 58 rotate synchronously with the shaft 60 as long as the worm gear 63 is held stationary. Rotation of the worm wheel 53 by acting on the idler 51 rotates the two-faced bevel gear 54 in the same direction and twice as fast as the movement of the worm wheel 83. The rotation of the two-faced bevel gear 54 acting through the pinion 55 rotates the bevel gear 81 and the adjusting member 58 in the op-' posite direction to the rotation of the worm wheel 53 and twice as fast as the movement of the worm wheel 53. In this gear train as in the others the shaft and the worm wheel 63 may be rotating simultaneously. I

Another example of a gear train suitable for use with a variable speed transmission is illus-=v trated in Figure VI. In this gear train a spur gear 10 keyed to a shaft ll meshes with spur pinions I2 carried on studs 13 projected laterally from a worm wheel 14. The worm wheel 14 is journaled on the shaft H adjacent the spur gear 10. An internally toothed annulus 15 carried from a hub 16 joumaled'on the shaft H adjacent the spur gear 10 meshes with the idler pinions 12. The annulus 15 has beveled gear teeth 11 on one side which mesh with an idler pinion l8 journaled on a stationary axle 19. The idler pinion meshes with and drives a bevel gear 80 keyed to an adjustingmember 81 in which a series of rods 82 are studded so that .they may rotate halves 83 of V-pulleys on threaded sleeves 84 and thereby effect changes in pitch diameter. The numbers of teeth in the various gears of the train are selectedso that a 1:1 velocity ratio is attained between the spur gear 10 and the adjusting member 8| with like rotational direction. This gear train operates in the same manner as those previously described and accomplish'es the same results.

The torque exerted by the pulleys on either of the shafts produces friction between the pulleys 1 The gears are required tric with respect to its shaft. When this is donethe velocity ratio through the gear train varies cyclically with the rotation of the eccentric numher. This variation tends to cause the driven gear, which may be the gear connected to the adjusting member, to oscillate slightly with respect to the shaft on which it is journaled. If there is no backlash in the gear train the eccentricity of one gear would produce a positive oscillation of the adjusting gear on the shaft but when a small amount of backlash is allowed it nrnvides a "lost motion connection between the j a 7 driving and driven gear such that ferce is applied through the gear train only at the ends of the cycle of oscillation. By making the backlash slightly greater than the oscillation produced by i the eccentric gear the gear train tends to move the adjusting member only during the points of maximum amplitude of the superimposed oscillation and the gear train runs idle during the remainder-the greater portion-of the time.

ment of the pulley halves on one shaft is precisely equal and opposite to the axial motion of the pulley halves on the other shaft. If these pulleys have conical faces the change in pitch diameter is exactly proportional to the axial shift of the pulley halves. When the pulleys are mounted on fixed center to center distances and the change in pitch diameter is exactly proportional to the axial motion it is found that if the belt length is adjusted to give the proper tension when one pulley is adjusted to its maximum pitch diameter and the other to its minimum pitch diameter that the belt will be loose when the pulleys are adjusted to equal pitch diameters.

is equal to are sin Z To apply this equation to the design of a suitable pulley face let Ra represent the pitch radius when the pitch diameters of the two pulleys are equal, i. e.,- unity speed ratio. The slope of the pulley face must be selected to match the V-belt to be used. Let a represent the angle between a line tangentto the pulley face at Re. and the axis of the pulley. Also let m represent the axial shift of the point of contact of the pulley and belt as the pitch radius changes. An inspection of Equation 1 indicates that, when the changes in pitch radius are equal and opposite, the increase in belt length is generally proportional to the square of (Rr). A parabola having.its axis of symmetry perpendicular to the pulley axis sati'sfies this condition.

The general equation of a family of parabolas on this axis is: 1/) The tangent to those parabolas passing through Ra at the radius Re is:

From this the equations representing the values of R and 1- may be derived in terms of the parab- Thus substituting in Equation 2:

Solving for R and r gives:

15 From these equations:

5 Rr=pL and arc sin Z Substituting these values in Equation 1 gives:

=arc sin 7:

R is larger than 1 because the tangent of a, the slope of the tangent line, is-negative. Since p is equal to 2m tan a these equations represent the exact values for the radii of the pulleys for various 'values of m.

To determine the constants of the parabola, in which the unknown terms are a and K, first solve the expression for 4L(1 p arc sin p-y/l-zfl) Since the term in parentheses cannot be expressed as an exact function it is impossible to write the equation of one parabola which will fit the theoretical curve along its full length. However a parabola can be'drawn through any three points of the theoretical curve. The coeflicients to give this parabola may be found b substituting the selected value of m in Equation 9, rernembering that p is a direct function of m. Having found a and having previously selected a and R, K may easily be found by substituting olas and m, the axial shift in the .1: direction.

. 9 into the equation of the slope of the tangent line and solving for K. Thus:

(10) K=Ra+a 173.11 c:

Having found the equations representin R and r, the ratio between maximum and minimum speeds may be easily derived. The maximum output speed is R/r times the input speed, while the minimum output speed is r/R times the input speed. The ratio of these speeds is R/r divided by r/R, i. e., (R/r) In this derivation it was assumed that the radial deviations from the line tangent to the pulley face were the same for an increasin radius as for a decreasing radius. This is an arbitrary condition because the deviations from a true cone required to maintain correct belt tension may all be applied to that limb of the curve defining R,

leaving r defined by the tangent line through'Rs.

This can be done by multiplying the last term of Equation 5 by 2, and dropping the last term of Equation 6. This is only one of many possible variations because only the average value of the radii is fixed.

Using a parabola to define the pulley face affords another advantage in that the slope ofthe face decreases for larger radii and increases for smaller radii. This corresponds generally to the change in cross sectional outline of a V-belt as it passes around a pulley. Rubber, a common material for the body of a belt, is nearly incompressible. When it is used to absorb shock it is. allowed freedom to expand at right angles to the line of action of the force through it. Without this freedom it is very stifl and unyielding. As a V-belt has a cord or wire center to prevent stretching, its inner face must expand sideways when it is wrapped around a pulley thereby decreasing the angle between its sides. The amount of this change is generally proportional to the radius of the pulley and is matched by the change in slope of the belt contacting part of the improved pulley shape. Therefore, with the improved pulleys, the belt runs in full contact with the V -pu.lley regardless of pitch radius.

Having described the invention, 1 claim:

1. In a device of the class described, in combination, a case, a partition dividing the case into compartments, a pair of shafts extending through l the case and partition in parallel alignment, a plurality of threaded members keyed to the portions of the shafts enclosed in one of the compartments, generally cone faced disks having threaded hubs supported on the threaded memnect each ring to its shaft to permit rotative ad-' iustment of the ring with respect to the shaft for adjusting the pitch radii of the pulleys.

2. In a device of the class described, in combination, a pair of parallelly d sp sed shafts, a plurality of generally cone faced disks mounted on the shafts and cooperating to form pulleys, threaded members for holding the disks in spaced relation and for varying the spacing to vary the pitch radii of the pulleys, a planetary gear sys Number tem journaled on each shaft intermediate its ends, each planetary gear system comprising a first portion keyed to the supporting shaft, a second portion that engages an adjusting member and is rotatable independently of the rotation of the shaft, and a third portion that is operatively connected to said threaded members through a gear train including a member journaled on a fixed axis, said planetary gear system being proportioned so that thethreaded members are held stationary-with respect to the disks when the adjusting memberis stationary and are rotated relative to the disks according to rotation of the adjusting member.

3. In a device of the class described, in combination, a pair of parallelly disposed shafts, right and left hand threaded members keyed to the shafts, a plurality of generally cone faced disks threadedly mounted on said members, a ring mounted on each shaft, a plurality of rods extending from the rings and engaging the disk, a planetary gear system journaled on each of said shafts, each gear system comprising one portion that is keyed to the supporting shaft, another portion that engages an adjustable element, and another portion that engages a geared member journaled on a fixed support and meshing with a gear attached to said ring,'the portions of the planetary gear systems being proportioned to drive the rings in synchronism with the shafts when the adjustable element is stationary and rotates the rings relative to the shafts when the adjustable element is operated.

4. In a device of the class described in whichv the pitch radius of a V-belt pulley is varied by axial adjustment of cooperating cone faced disks forming the pulley, in combination, a shaft on which the pulleys are mounted, threaded means for holding the disks in axial spaced relation, 9. planetary gear train having a sun gear keyed to the shaft, a planet carrier that is journaled on the shaft and that has planet pinions meshing with the sun gear, adjusting means for rotating the planet carrier independently of rotation of the shaft, an annular gear rotatively journaled on the shaft and meshing with the planet pinions, and gearing that includes a gear journaled on a fixed axis for operatively connecting the annular gear to-the threaded means, said planetary gear train causing the threaded means to change the pitch radius of the pulleys only when said planet car-' rier is rotated.

ROBERT D. MORSE.

REFERENCES CITED The following references are. ofrecord in the file of this patent:

UNITED STATES PATENTS Name Date Given et al; Mar. 13, 1894 Reeves May 25, 1897 Adams June 6, 1933 Heyer Mar. 5, 1935 Number Weston May 9, 1939 2,348,994

Otto May 16, 1944 FOREIGN PATENTS Country Date Fraser Dec. 14, 1937 Great Britain Dec. 9, 1920 

